Fuel injection pump



Allg. 9, 1949. C, EDWARDS 2,478,528

FUEL INJECTION PUM? Filed Aug. 22, 1946 4 Sheets-Sheet l 99 *UZ HIS ATTORNE S.

Aug 9, 1949 H. c. EDWARDS FUEL INJECTION PUMP 4 Sheets-Sheet 2 Filed Aug. 22

AlT mm N o QQ AWS INVENTORZ im@ C.,

www

l HRS ATTORNEY Aug. 9, 1949.

H. C. EDWARDS FUEL INJECTION PUMP Filed Aug. 22, 1946 4 Sheets-Sheet 5 H\S ATTORNEYS.

Aug. 9, 1949- H, c. EDWARDS FUEL INJECTION PUMP 4 Sheets-Sheet 4 Filed Aug. 22, 1946 INVENTOR l M HIS ATTORNEYS Patented Aug. 9, 1949 FUEL INJECTION PUMP Herbert C. Edwards, Canal Fulton, Ohio, assigner to The Timken Roller Bearing Co., Canton. Ohio, a corporation oi' Ohio Application August 22, 1946, Serial No. 692,299

18 Claims.

This invention relates to pumps, particularly single plunger fuel Injection pumps for multicylinder compression ignition engines. The invention has for its principal objects to provide a simple, economical and compact pump of the above type that will deliver a correct quantity of fuel to each working cylinder of the engine in proper timed relation to the working cycle thereof; that is adjustable to vary the timing and quantity of the fuel injection; that will provide for automatically controlling the' quantity of the fuel injection in accordance with the speed of the engine; that will provide for setting the fuel quantity control means for different engine speeds; that will provide a unit injection and supply pump assembly in which the supply pump is operated by the injection pump; and that will obtain other advantages hereinafter appearing. The invention consists in the governor controlled unit injection and supply pump and in the parts and combinations and arrangements of parts hereinafter described and claimed.

In the accompanying drawings, which form part of this specification and wherein like symbols refer to like parts Wherever they occur,

Fig. l is a top plan view of a governor controlled fuel pump embodying my invention,

Fig. 2 is a side elevational view of the control lever side of said pump,

Fig. 3 is an end elevational view of the supply pump end of said pump,

Fig. 4 is an enlarged central vertical longitudinal sectional view on the line 4 4 in Fig. 5,

Fig. 5 is an enlarged vertical cross-sectional view through thesupply pump end of the pump, the section being taken on the line 5-5 in Fig. 2,

Figs. 6, '7, 8, 9 and 10 are vertical cross-sectional views on the lines Ii-6. 'I--1. B-8, 9-8 and Ill-Ill, respectively, in Fig. 4,

Fig. 11 is a fragmentary vertical longitudinal sectional view on the line II-II in Fig. 'l' and Fig. 12 is a vertical cross-sectional view on the line I2-I2 in Fig. 4.

The single plunger, governor controlled, multiple injection fuel pump shown in the accompanying drawings is adapted for use with a sixcylinder, four-cycle, compression ignition engine (not shown). Said fuel injection pump comprises an elongated oil containing housing I having axially alined cylindrical end openings 2 and 3, respectivelyI and a top opening I closed by a removable cover plate 5 having a hooded breather opening 5 therein. A drive shaft 6 extends into the housing I through the end opening 2 thereof and is adapted to be driven by or in unison with the engine at one-half engine speed. The drive shaft 6 is supported in two rotary antifriction bearings, preferably taper roller bearings 1 and 8, mounted respectively in a cover or cap 9 for the outer end of the end opening 2 of the housing I and in a cross wall I0 formed in said housing intermediate between the ends thereof. The end cap 9 is removably secured to the housing I by means of socket head cap screws II and has a cylindrical plug portion 9a that ilts within the end opening 2 of said housing. A suitable oil seal I2 surrounds the drive shaft B between the outer end of the end cap 9 and the inner raceway member of the roller bearing 1.

Mounted in the end opening 2 of the housing I in endwise abutting relation to the inner end of the plug portion 9a of the cap B for said opening is an annular holder I3 which surrounds the shaft B and supports three circumferentially spaced conical cam rollers I l that are disposed radially of said holder and taper inwardly towards the axis thereof. The conical cam rollers I4 are located in pockets I5 provided therefor in the annular holder I3 and are journaled on pins I6 mounted in radial bores provided therefor in said holder. A dowel pin I1 extends through the end cap 9 lengthwise thereof and terminates at its inner end in a crank portion Ila which tits Within a radial slot IB provided therefor in the adjacent end of the annular roller holder I3. By turning the dowel Il, the roller holder I3 may be rotated in the supporting opening 2 therefor In the housing I, after which said dowel and said roller holder may be locked in the desired position of rotary adjustment by means of a nut I'Ib threaded on the exposed outer end of said dowel. The drive shaft B has an enlarged tubular inner end portion 6d on which is mounted an annular cam member I9 having a conical cam face 20 at its holder opposing end with six circumferentially spaced peaks 20a adapted to successively engage three cam rollers Il journaled in the holder I3. The annular cam member I 9 is splined to the shaft B for rotation therewith and for axial sliding movement relative thereto by the cam rollers Il, the cam member being forced inwardly along the large tubular end portion 6a of said shaft when a rise or peak 20a on the cam face 2li of said cam member engages a cam roller Il. The splined connection between the cam member I9 and the enlarged tubular inner end portion Ba of the shaft 6 preferably comprises longitudinal ribs 2| that are formed in said cam member and fit in longitudinal slots 22 in said enlarged tubular end portion of said shaft. The rotary and axially slidable cam member I3 is yieldably held in engagement with'the cam rollers I4 .by means of a coil compression spring 23 that is mounted around the enlarged tubular inner end portion la of the drive shaft 8 with one end seating against said cam member and with the other end seating against the opposing end face of a hexagonal edge cam 24 nxed to said tubular portion between a collar 25 thereon and the adjacent end of the inner raceway member of the roller bearing 8.

Extending into the tubular inner end portion a of the drive shaft 6 through the open inner end thereof is a pump plunger 28 which rotates with said tubular end portion but is reciprocated axially therein by the annular cam member i3 splined thereon. The reciprocating motion of the cam member i8 is imparted to the pump plunger 26 through a transfer plate 21 which is mounted in the reduced blind end of the tubular portion of the drive shaft 5 and has an undercut slot 21a, which opens through one side of said plate and is adapted to rotatably receive the adjacent headed end 28 of said plunger, and exterior lugs 28 that fit in cross notches 31| in the internal ribs or splines 2| in the drive shaft receiving bore of said cam member and are slidable with said splines in the longitudinal slots 22 in said tubular portion of said drive shaft.

The rotary driving connection between the drive shaft 8 and the cam reciprocated pump plunger 28 comprises a sleeve 3| ysupported in the enlarged tubular end portion Ba of said shaft 5, diametrically opposed pins 32 fixed to said tubular end portion of said plunger and extending radially inwardly thereof into left-hand helical slots 33 formed in said sleeve, and a ring or spider 34 that is secured to said pump plunger by means of a diametre] pin 35 rigid therewith and has peripheral lugs 38 that are located on a diameter at right angles to said pin and fit in straight longitudinal slots 31 provided therefor in said sleeve between the helical slots 38 therein. By this arrangement, the plunger 26 is adapted to rotate with the shaft 5 while being reciprocated axially thereof by the cam member i8 and the pin-andhelical slot connections between said shaft and the sleeve 3| produces relative rotation of said nplunger and shaft when said sleeve is slid axially of said shaft in either direction. The pin 35 xed to the plunger 26 is axially slldable in the openings provided therefor in the ring .34 so as to accommodate misalignment of said plunger and still drive said plunger at the same velocity of rotation as the shaft l.

'I'he rotary and reciprocable pump plunger 26 works in a pump cylinder or barrel 38 having an enlarged intermediate portion 33 that nts within the end opening 3 in the pump housing i and a larger head portion 4i! that abuts endwise against the outer face of said housing around said end opening. The outer end of the axial pump plunger receiving bore of the pump cylinder or barrel 38 is closed by means of a threaded plug 4I, and the working end of the plunger 2li cooperates with said bore to form a pressure chamber or space 42 at the closed outer end thereof. The pump barrel 3B has a plurality of fuel delivery or discharge passageways 43 therein, one for each of the six working cylinders of the engine supplied by the pump. The fuel discharge passageways 43 are spaced apart equally about the axis of the pump barrel or cylinder 33 with their inner ends opening into the plunger supporting bore inwardly of the pressure chamber 42 and with their outer ends opening through the outer end face of the head 48 of said cylinder where they are threaded for connection with fuel in- Jection lines or conduits 44 that lead to the fuel injection nozzles (not shown) for the respective working cylinders of the engine. The pump cylinder 33 also has a single combination fuel inlet and l'uel by-pass passageway 45 therein whose inner ,end opens into the plunger supporting bore inwardly of the inlet ends of the fuel discharge passageways 43 and whose outer end opens outf wardly through the peripheral surface of the enlarged head end 48 of said pump cylinders.

The pump plunger 26 has an annular groove 48 therein adjacent to the working end thereof andadapted, in the retracted position of said plunger, to communicate with the single combination inlet and by-pass passageway 45. The plunger 26 also has six equally spaced longitudinal fuel inlet and pressure relief grooves 41 in .the periphery thereof that lead rearwardly from the rear edge of the annular peripheral groove 46 far enough to establish communication between the fuel inlet and by-pass passageway 45 and said annular groove during the entire length of either the suction or pressure'stroke of the plunger when any one of the six longitudinal grooves is in communication with said fuel inlet and by-pass passageway. The injection pump plunger also has a single longitudinal peripheral indexing distributing groove 48 that extends from the annular groove through the working end of the plunger 26 and is adapted to provide continous communication between said annular groove and the pressure chamber 42 at the working end of said plunger. When the plunger 28 is rotated, the single peripheral distributing groove 48 therein is adaptedeto successively register with the six discharge passageways 43 in the `pump cylinder 38 during the reciprocating movement of said plunger, and the six longitudinal metering and pressure relief grooves 41 are adapted to successively register with the fuel inlet and by-pass passageway 45.

The barrel or cylinder 38 of the fuel injection pump is held in the end opening 3 of the pump housing I by means of an end cap or plate 43 which is secured by socket head cap screws 50 to the adjacent end of said housing and has a cylindrical hole therethrough adapted to snugly receive the cylindrical head portion 40 of said pump barrel or cylinder. The hole in the retainer plate or cap 49 has an annular lip or flange 5I at the outer end thereof that overlaps the head 40 of the barrel member 38 and retains the same in said hole. The barrel member 38 is prevented from rotating in the plate 49 by means oi a dowel pin 49a which is fixed to said plate and fits within a recess provided therefor in the head 48 of said barrel member. The head supporting opening in the retaining plate is sealed against leakage by two sealing rings 52 located therein, one on each side of the outer end of the fuel inlet and by-pass passageway 45 in the barrel head 40.

The pump chamber 42 is supplied with fuel by a supply pump mechanism operated from the drive shaft 6 of the fuel injection pump. 'Ihis supply pump comprises a double acting piston 53 mounted in a bore 53a that extends through the retaining plate 49 from side to side thereof crosswise of the barrel head 48 supported therein. The piston 53 is reciprocated by means of a rocker shaft 54 that is located in the housing I above and parallel with the drive shaft 6 and plunger 28 and extends through the pump barrel supporting end wall of said housing and is iournaled in a suitable bushing 55 provided therefor in said end wall. The outer end of the bushing receiving opening is counterbored to receive a suitable annular oil seal 55, which bears axially against the outstanding ilange of a collar 55a mounted on the rocker shaft 54 between a crank 51 thereon and the bushing 55. The crank 51 operates in a recess 55 in the inner face of the plate 49 and has a pin 59 that ts within a cylindrical opening provided therefor in a square bushing 55 mounted in a square opening that extends through the piston 53 transversely thereof, whereby said piston is adapted to be reciprocated when said rocker shaft is oscillated. The inner end of the rocker shaft 54 is journaled in a bushing 5| provided therefor in the cross wall i5 of the housing and said shaft is provided adjacent to said wall with a rocker arm 52 having a cam roller 53 journaled on the free end thereof. The cam roller 53 cooperates with the hexagonal edge cam 25 which is fixed to and rotates with the drive shaft 5, whereby said rocker shaft is oscillated by the rotary movement of said drive shaft.

Fuel from a tank or other source of supply (not shown) is supplied to one end of the supply pump piston supporting bore through an inlet iltting 54 threaded therein. The inlet iltting opposing end of the supply pump piston 53 has a spring closed, inwardly opening disk valve 55 therein. Inwardly of this inlet valve 55, the supply pump piston 53 has a radial port 65 therein which opens upwardly into a vertical priming pump chamber or cylinder 51 through a port 55a in the bottom or lower end thereof. Reciprocable in the priming pump chamber 51 -is a normally inoperative piston 55 having an opening extending longitudinally therethrough that is normally closed by an upwardly opening, spring seated, disk valve 59 The priming pump piston 55 has an actuating rod 15 extending upwardly therefrom through a bushing 1| that is threaded into the upper end of the priming pump cylinder or chamber 51. An operating knob 12 is removably secured to the exposed upper end of the piston rod by means of a screw 13 and is threaded on the upper end of the piston rod bushing 1| so as to lock the priming pump piston 55 in the lower end of the cylinder 51.

The priming pump cylinder 51 communicates at its upper end with an outlet iltting 14 that is threaded into the end plate 49 above the inlet iltting 54. The outlet tting 14 communicates through a suitable conduit 15, which may include a illter (not shown) with an inlet fitting 15 that is threaded into the cross bore 53a at the end thereof opposite the inlet fitting 54. This end of the bore 53a has a spring seated inwardly opening inlet valve 11 mounted therein inwardly of the inlet fitting 54. The bore 53a is interrupted between the inlet valve 11 and the piston 53 to form within the end plate 49 a chamber or cavity 15 which extends around the head 45 of the fuel injection pump cylinder or barrel 35 and is in continuous communication with the end of the inlet and by-pass passageway 45 which opens through the peripheral surface of said head of said cylinder or barrel. Interposed between the inlet valve 11 and the opposing end of the piston 53 is a coil compression spring 19 which has one end seated in a recess in said end of said piston and the other end supported in a spring seat member 55 mounted in the bore 53a inwardly of said inlet valve. The piston 53 is reciprocated in one direction against the pressure of the spring 15 by means of the cam actuated rocker shaft 54 and in the other direction by means of said spring, which also serves to hold the roller 53 on the inner end oi' the rocker arm 52 of said shaft in engagement with the cam surface of the hexagonal cam 24 which rotates with the drive shalt 6. By this arrangement, the piston 53 operates in one direction o! its reciprocating movement to draw fuel through the inlet valve 55 in said piston, thence through the inlet valve 55 in the locked priming pump piston 55 into the cylinder 51 therefor, thence from the priming pump cylinder through the conduit I5 to the inlet iltting 15, thence through the valve 11 into the chamber or cavity 15 in the end plate 45. In the other direction of its reciprocating movement, the piston 53 operates to force the fuel in the chamber or cavity 15 into the inlet and by-pass passageway 45 which opens into the cylinder 35 in which the injection pump plunger 25 operates. i

The barrel end plate 49 also has a horizontal bore 5I therein above the level oi the supply pump piston 53 and at one side of the priming pump chamber 51. The outer end of the bore 5| is closed by means of a threaded plug 52; and said bore communicates through a port 53 near its closed outer end with the fuel chamber 15 and through a port 54 at its inner end with the priming pump chamber 51 above the level of the normally inoperative piston 59 therein. Reciprocable in the bore 5| is a loosely fitting piston 55 for equalizing the pressure developed by the fuel supply piston 53. This pressure equalizing piston 55 is urged by means of a coil compression spring 55 against a stop stud 52a that projects axially from the inner end of the plug 52 for the outer end of said bore. The axial stud 52a of the closure plug 52 for the bore 5| holds the spring pressed piston 55 therein clear of the port 53 which establishes communication between said bore and the recess or chamber 15 that communicates with the inlet and bypass passageway 45. Thus, the discharge from the outer end of the supply piston 53 has access to the spring supported end of the pressure equalizing piston 55 through the port 54, while the pressure developed by the inner end of said supply pump piston is transmitted to the other end ol said pressure equalizing piston through the port 53. By this arrangement, if the pressure developed at one end of the supply pump piston 53 greatly exceeds the pressure at the other end thereof, the small piston 55 is deflected toward the least pressure. Usually the higher pressure is on the inner end oi' the fuel supply piston 53, so that the spring 55 is compressed a certain amount. Thus, during operation, the small pressure equalizing piston 55 floats in the bore 5| clear of the stop stud 52a in the outer end thereof.

Located in a horizontal bore 51 in the barrel end plate 451ust above the pressure equalizing piston 55. is a small fuel by-pass or pressure relief piston 55. The outer end of the bore 51 is provided at its outer end with an outlet fitting 59, while the inner end of said bore opens into the priming pump chamber 51 above the normally inoperative piston 55 in the lower end thereof. `The by-pass piston 55 is normally pressed inwardly in its supporting bore 51 against a diametral stop pin 9| therein by means of a coil compression spring 92 that has one end seated in the outer end of said piston and the other end seated in the inner end of the outlet iitting 55. The bore l1 has an annular groove 93 therein which extends around the piston 59 and opens into a longitudinal groove 94 that extends to the outlet tting 55 in the outer end of said 15 bore. The piston Il operates as a pressure reguananas lating device and is normally held against the stop pin i by the pressure oi the spring l2 and in covering relation to the annular escape groove 5I. However, as the pressure generated on the outer end of the supply pump piston 53 increases, the piston Il is forced outwardly in the bore I1 against the pressure of the spring 92 until said piston uncovers the annular groove 53 in said bore and allows the fuel to by-pass or escape through the longitudinal groove 54 to the outlet fitting 55 where the surplus fuel is returned to the source of fuel supply through a conduit 35.

When it is desired to prime the fuel injection pump, the operating knob or handle 12 of the priming pump is unscrewed from the bushing 1| and used to manually reciprocate the priming piston 55. This action draws fuel in through the inlet fitting 54 through the valve 65 in the supply pump piston 53, through the valve 59 in the priming pump piston 45 and through the conduit 15 and the valve 1l into the chamber or cavity 13 which communicates with the inlet. and by-pass passageway 45 of the fuel injection pump. When the Irnob 12 is screwed down tightly in its lowermost position, the valve 59 in the priming piston 55 acts after the manner of the valve 55 in the supply pump piston 53, thereby providing a double valve in the discharge side of the supply pump and thus forming a double seal which prevents back flow of pressure from the discharge side of the supply pump.

The operation of the hereinbefore described unit injection and supply pump assembly is as follows: The drive shaft 5 is continuously rotated from the engine at one-half engine speed and the fuel injection plunger 25 rotates with said drive shaft while being reciprocated in the pump barrel or cylinder 36 by a roller actuated cam member i6 splined on said shaft, the pump plunger making one complete rotation for each engine cycle. The six peaks 26a of the cam 20 of the cam member IB cooperate with the three cam rollers i4 so that the plunger 2B makes six reciprocating cycles for each rotation thereof. The multiple cam face and rollers I4 serve to distribute the injection load around the axis of the plunger 26 and provide a maximum length of roller pin and roller and cam contact. At the same time, the rocker shaft 54 is operated by the hexagonal edge cam 24 on the shaft 6 to impart one complete reciprocating cycle to the supply pump piston 53 for each reciprocating cycle of the injection plunger 26. This reciprocating movement of the supply pump piston 53 causes fuel from the supply tank to be drawn through the inlet valves 65, 6B into the priming pump chamber 61, thence through pipe 15, which contains a fine filter (not shown) and thence through the inlet valve 11 into the fuel chamber 1l where the fuel is forcedV by said piston into the inlet and by-pass passageway 45 which communicates with the pressure space or chamber 42 of the fuel injection pump through the grooves 45, 41 and 4B in the plunger 26.

During each pressure stroke of the plunger 26, fuel is forced through a discharge passage 43 when the rear edge of the annular groove 45 in said plunger closes the inlet and by-pass passageway 45 and the distributing groove 48 of said plunger registers with said discharge passageway. Fuel injection through this discharge passageway 43 ceases while the pump plunger 26 is still operating on its pressure stroke, and while the distributing groove 48 is still in communication with the discharge passageway 43, when one of the six pressure relief grooves 41 registers with the inlet andby-pass y45. Atthlspolntinthe pressure stroke of the rotating plunger 25, there is a back flow of the fuel from the discharge passageway 4I to the chamber 15 through the pressure chamber 42, distributing groove 45. annular groove 45, pressure relief groove 41 and inlet and by-pass or overow passageway 45, thereby reducing the pressure in the discharge passageway 43 to the supply pump pressure and thus preventing norzle dribble.

As stated above. the piston serves to equalize the pressure at opposite ends of the dou-ble acting supply pump piston 53, while the piston 5l serves to Ilay-pass the surplus fuel through the fuel return pipe 55. Any air which collects in the fuel chamber 15 rises to the top of said chamber and slowly escapes through the port I3 into the bore 8| having the loosely fitting pressure equalizing piston 85 therein and thence around said piston and the pressure relief piston 55 to the fuel return conduit 95. 0n the return or suction stroke of the plunger 2B, the positive stroke of the supply pump piston 55 is taking place. which stroke forces the fuel from the chamber 18 into the inlet and by-pass passageway 45 to illl the chamber or space 42 formed by the suction stroke of said plunger. The pump may be adjusted to vary the timing of the fuel injection by turning the dowel pin I1 so as to rotate the cam roller holder I3 relative to the cam member i9.

The quantity of fuel discharged through the discharge passageways 43 may be varied by shifting the sleeve 3l axially in the tubular inner end portion 6a of the drive shaft and thus bring about an angular adjustment of said sleeve and the plunger 26 relative to the drive shaft and a similar angular adjustment of the pressure relief groove 41 in said plunger relative to the inlet and by-pass passageway 45. Thus. if one of the pressure relief grooves 41 of the plunger 26 is in register with the inlet and by-pass passageway 45 during the entire working stroke of said plunger, the fuel is discharged through said passageway and not through the discharge passageway 43. When, however, the sleeve 3i is shifted axially the time of the opening of the passageway 45 is delayed, thus causing a delivery of fuel through the fuel discharge passageway 43. The fuel quantity control sleeve 3| is adjusted axially of the drive shaft 6 therefor by means of a. centrifugal governor mechanism that is responsive to the speed of said shaft. This governor mechanism preferably comprises a spider 66, which is mounted on the end of the tubular inner end portion 6a of the drive shaft 6 and has a resilient rotary driving connection therewith. This connection comprises two helical coil springs 91 mounted in an external annular groove 91a in the drive shaft 6, a. key 99 xed to said drive shaft and interposed between two adjacent ends of the springs 91 and a screw IDI) threaded through the hub of the governor spider 96 and extending into said groove between the other two adjacent ends of said springs. This arrangement provides a resilient drive which absorbs or cushions shocks due to variation in angular motion of the rotating parts caused by the different injection impulses which take place during rotation.

Supported on pivot pins IBI mounted in the spider transversely of the rotary axis thereof is a series of centrifugal weights |02 that are grouped around a thrust spool |53 that is sleeved on the barrel member 38 for sliding movement axially thereof and are adapted to swing outwardly away from said spool under the action of asvasas centrifugal force from the axis about which the spider rotates. The thrust spool |03 serves to limit the inward swinging movement of the weights while the outward swinging movement thereof is limited by stops |04 formed on the spider. The thrust spool |03 is located opposite the inner end of the drive shaft 6 in endwise abutting relation to a thrust collar or ring |05 that is mounted for rotary but non-axially sliding movement on the exposed end of the fuel quantity control sleeve 3|. The connection between the thrust ring |05 and the sleeve 3| comprises a split ring that nts in annular grooves provided therefor in said ring and sleeve. The pivot ends of the centrifugal weights |02 have fingers |01 that extend inwardly therefrom on one longitudinal side edge thereof and have curved surfaces |00 adapted, when said weights swing outwardly, to bear against the rotary thrust collar on the control sleeve 3| and thus shift the latter axially in the tubular end portion 6a of the drive shaft 0, whereby the pin-and-helical slot connections 32, 33 between said sleeve and the drive shaft 0 serve to change the angular relationship of said shaft and sleeve and thus vary the quantity of fuel delivered by the plunger 20 through the fuel delivery passageways 43.

The outward swinging movement of the centrifugal governor weights |02 shifts the fuel control sleeve 3| axially of the drive shaft 0 in a direction that will decrease the quantity of fuel delivery. When the governor weights |02 swing inwardly due to a decrease in speed of the drive shaft 0, the sleeve 3| is shifted axially in the tubular end portion a of the drive shaft 0 in the direction of increased fuel delivery by means of a governor control system enclosed within the housing and adjustable from the exterior thereof. This governor control system comprises a thrust yoke |09 which is rotatably supported for vertical swinging movement longitudinally of the thrust spool |03 on a cross-shaft I0 that extends from side wall to side wall of the housing I above the level of said spool and is journaled in said side walls with one end bent at right angles to form an operating handle i located exterioriy of said housing. The two downwardly extending branches of the `thrust yoke |09 straddle the rocker shaft 54 and the pump barrel 30 and terminate at their lower ends in forwardly curved fingers ||2 that seat against the thrust spool |03 at the end thereof remote from the end that bears against the thrust collar |05 carried by the sleeve 3|. The upper end of the thrust yoke |09 has a stop screw ||3 threaded therethrough which abuts against a seat ||4 provided therefor in the adjacent end wall of the housing and serves to limit the swinging movement of the fingers ||2 of the depending arms of said yoke in the direction of the governor spool |03. This stop screw serves to limit the inward travel of the governor weights |02 and the sleeve 3| and thus constitutes a limiting stop for the maximum usable quantity of fuel.

The governor control system also includes a control shaft ||5 that extends from side Wall to side wall of the housing I above the cam seating spring 23 and has its ends journaled in bearings ||9 that project inwardly from said side walls and has one end located exteriorly of said housing and provided with a control lever whose swinging movement is limited in one direction by a stop screw ||0 threaded in said housing on one side of said lever and in the other direction by a stop screw llt threaded into said housing on the other lns 10 side of said lever. A control yoke |20 has V- notches |2| in the lower ends of its downwardly extending branches; and these notched ends are supported on knife edges I 22a formed on the upper ends of pins |22 that are supported in vertical bores formed in lateral extensions of the control shaft bearings H0. The knife edges |22a are located at one side of the control shaft H5 on the side thereof remote from the thrust yoke |09; and said control yoke |20 has a lug |23 projecting laterally and thence downwardly from the top thereof in overhanging relation to said control shaft l i5. The control yoke shaft ||5 has a lug |24 extending upwardly therefrom for rotation therewith. A coil tension spring |25 has its upper end hooked into an opening provided therefor in the top of the yoke |20 and has its lower end hooked into an opening provided therefor in the upwardly projecting lug |24 on the control shaft. Extending longitudinally of the housing above the supply pump actuating rocker shaft 54 and between the thrust yoke |09 and the control yoke |20 is an extensible link comprising a rod |20 and end ttings |21 axially slidable thereon and terminating at their remote ends in pointed or tapered portions |20. A coil compression spring |29 is sleeved on the axially extensible link with its ends iixed to the end members |21 thereof and tends to force them apart and hold them one with its pointed end |20 rockably supported in a conical recess |30 in the thrust yoke |03 and the other with its pointed end similarly supported in a similar recess |3| in the control yoke |20. The control lever Ill may be operated to compress the oil compression spring |29 to keep the fingers ||2 of the thrust yoke |09 in contact with the governor spool |03 through the tension spring |25, the upper end of which is attached to the control yoke |20 and the lower end of which is attached to the lug |24 on the control shaft H5. As the lug |20 is rotated toward the drive end of the pump, it swings in an arc which, at its extreme, passes through the knife edge center of rotation |22a of the control yoke |20. In this position of the lug |24 the tension spring |25 has no effect on the governor spring system. As the control shaft lug |24 is rotated in the other direction away from the drive end of the pump, the effective lever arm in the line of action of the tension spring |25 increases. At the same time, the length of the tension spring |25 is increased, thereby increasing the load of said spring and transferring such additional load through the compression spring 29 to the thrust yoke |09 and thus increasing the load applied to the governor spool |03 to keep the centrifugal governor weights |02 in closed position. By reason of this additional spring load on the governor spool a higher speed of rotation of the drive shaft 6 is required to enable the centrifugal weight force to overcome the spring force and shift the control sleeve 3| in the direction of decreased fuel delivery. Thus, by adjusting the control lever the spring combination |25 and |23 may be regulated to match the centrifugal weight force so as to provide a higher spring weight at higher speeds as well as a higher spring load. For example. if both lever arms of the thrust yoke are of equal length. the combined effective rate of both springs along the line of action on the control sleeve 3| will vary inversely as the square of the ratio between the tension and compression spring lever lengths. For each speed setting of the control lever H1, there are two position of axial adjustv yposition corresponding above, the compression spring |2I and the tension ananas ment of the fuel control sleeve 3|, one position corresponding to wide open throttle and the other to no throttle. As stated spring |25 cooperate to produce an over-all spring rate that matches the weight forces, which are combined through the lever arms about the knife edges. The governor control system provides constant governor regulation over a wide range of engine speeds, and the forces required to adjust the system to any given speed are small as applied to the control lever ||`l and there are only two springs required.

The governor spool opposing faces of the depending arms of the thrust yoke |09 are formed just below the thrust yoke supporting shaft with nat seats |32; and said yoke supporting shaft has a block |33 fixed thereto that extends across said seats. By this arrangement, the exposed handle end I I of the yoke supporting shaft may be manipulated to so rotate the said shaft in a direction that will cause the ends of the block Il! thereon to bear against the seats |32 on the thrust yoke N9 and swing the latter in a direction that will overcome the pressure of the governor springs |25, |29 and allow the governor weights |02 to expand to their outmost position and moves the sleeve 8| to its outer position in the shaft 6, whereby all of the fuel is by-passed and there is no fuel delivery. Thus, the lever constitutes a shut olf lever to stop delivery of fuel regardless of the position of the throttle lever |I'l.

Obviously, the hereinbefore described unit goernor controlled fuel injection pump assembly admits of considerable modification without departing from the invention. Therefore, I do not wish to be limited to the precise arrangement shown and described.

What I claim is:

l. A fuel injection pump for a multi-cylinder internal combustion engine comprising a stationary cylinder having a combination fuel inlet and by-pass passageway opening into said cylinder through a single opening and a plurality of fuel discharge passageways, a plunger working directly in said cylinder, means for simultaneously reciprocating and rotating said plunger in said cylinder, means formed on said plunger for successively placing said discharge passageways in communication with the pressure space of said cylinder in intermittent successive positions of the rotary and reciprocating movement of said plunger, and means formed on said plunger and operable during each pressure stroke thereof for placing said pressure space first in communication with said inlet and by-pass passageway through said single opening thereof, then cutting of! communication between said pressure space and said single opening of said inlet and by-pass passageway and then reestablishing communication between said pressure space and said single opening of said inlet and by-pass passageway when any one of said discharge passageways is in communication with said pressure space.

2. The combination set forth in claim 1 wherein the means for rotating said plunger is adjustable to change the phase relationship between said plunger and plunger rotating means and thereby vary the quantity of fuel discharged through said discharge passageways, and said last mentioned means is automatically controlled by means responsive to the speed of rotation of said plunger rotating means.

3. A fuel injection pump for a multi-cylinder internal combustion engine comprising a sta- 12 tionary cylinder having a single combination fuel inlet and by-pass passageway opening into said cylinder through a single opening and a plurality of fuel discharge passageways, one for each engine cylinder, spaced apart equally about the axis of said cylinder, a plunger working directly in said cylinder. means for rotating said plunger in said cylinder. means for imparting to said plunger during each complete rotation a number of reciprocating cycles corresponding to the number of engine cylinders, means formed on said plunger for successively placing said discharge passageways in communication with the pressure space of said cylinder in intermittently successive positions of the rotary and reciprocating movement of said plunger, and means formed on said plunger and operable during the pressure stroke thereof for placing said pressure space first in communication with said inlet and by-pass passageway through said single opening thereof, then cutting off communication between said pressure space and said single opening of said inlet and by-pass passageway and then reestablishing communication between said pressure space and said single opening of said inlet and by-pass passageway when any one of said discharge passageways is in communication with said pressure space.

4. A fuel injection pump for a multi-cylinder internal combustion engine comprising a cylinder having a single combination fuel inlet and bypass passageway opening into said cylinder through a single opening and a plurality of fuel discharge passageways, one for each engine cylinder, a plunger working directly in said cylinder, means for simultaneously reciprocating and rotating said plunger in said cylinder, means formed on said plunger for successively placing said discharge passageways in communication with the pressure space of said cylinder in intermittently successive positions of the rotary and reciprocating movement of said plunger, and means formed on said plunger and operable during the pressure stroke thereof when any one of said discharge passageways is in communication with said pressure space for first cutting off communication between said pressure chamber and said inlet and by-pass passageway, then cutting off communication between said pressure chamber and said single opening of said inlet and by-pass passageway and then reestablishing communication between said pressure chamber and said single opening of said inlet and by-pass passageway, said means also establishing communication between said pressure space and said single opening of said inlet and by-pass passageway during the suction stroke of said plunger.

5. A fuel injection pump for a multi-cylinder internal combustion engine comprising a cylinder having a single combination fuel inlet and bypass passageway opening into said cylinder through a single opening and a plurality of fuel discharge passageways, a plunger working dlrectly in said cylinder, and means for continuously reciprocating and rotating said plunger in said cylinder, said plunger having an annular peripheral groove therein adapted to communicate directly with said inlet and by-pass passageway when said plunger nears the end of its suction stroke. a single longitudinal peripheral groove extending from said annular groove through the working end of said plunger and adapted to successively register with said discharge passageways in intermittently successive positions of the rotary and reciprocating movement of said plunger and a series of circumferentially spaced longitudinal peripheral grooves of a number corresponding to the number of discharge passageways extending from said annular groove far enough to establish communication between said annular groove and said single opening of said inlet and by-pass passageway in all positions of the reciprocating movement of said plunger.

6. The combination set forth in claim wherein the means for rotating said plunger is adjustable tochange the phase relationship between said plunger and plunger rotating means to thereby change the positions of said series of longitudinal grooves relative to said inlet and by-pass passageway and thus vary the quantity of fuel discharged through said discharge passageways and said mentioned means is automatically controlled by means responsive to the speed of rotation of said plunger rotating means.

7. A unit fuel injection and supply pump assembly for a multi-cylinder internal combustion engine comprising a fuel injection cylinder having a combination fuel inlet and by-pass passageway and a plurality of fuel discharge passage-v ways, a plunger working in said cylinder, means for simultaneously reciprocating and rotating said plunger in said cylinder, means formed on said plunger for successively placing said discharge passageways in communication with the pressure space of said cylinder in intermittent successive positions of the rotary and reciprocating movement of said plunger, means formed on said plunger and operable during each pressure stroke thereof for placing said pressure space first in communication with said inlet and bypass passageway, then cutting off communication between said pressure space and said inlet and by-pass passageway and then reestablishing communication between said pressure space and inlet and by-pass passageway when any one of said discharge passageways is in communication with said pressure space, a fuel supply cylinder communicating with said inlet and by-pass passageway, and a piston working in said fuel supply cylinder and operable by said plunger rotating means for feeding fuel to said inlet and bypass passageway.

8. The combination set forth in claim 'l wherein said fuel injection and supply pump assembly includes a priming cylinder that communicates with said inlet and by-pass passageway and a priming piston that is manually reciprocable in said last mentioned cylinder.

9. The combination set forth in claim 7, wherein said fuel supply cylinder communicates at both ends with said inlet and by-pass passageway, said piston is a double acting piston, means is provided for equalizing the pressure at both ends of said fuel supply cylinder, and means is provided for by-passing fue] from said fuel supply cylinder at a predetermined pressure at one end thereof.

10. A fuel injection pump for a multi-cylinder internal combustion engine comprising a cylinder having an inlet and by-pass passageway, a plurality of discharge passageways, a plunger working in said cylinder, means formed on said plunger for successively placing said discharge passageways in communication with the pressure space of said cylinder in intermittently successive positions of the rotary and reciprocating movement of said plunger, and means formed on said plunger for placing said pressure space in communication with said inlet and by-pass passageway during the suction and pressure strokes of said plunger, said plunger reciprocating and rotating means comprising a shaft adapted to be driven by or in unison with said engine, a cam operated by said shaft for reciprocating said plunger, and a connection between said shaft and plunger for rotating the latter, said connection being adjustable to change the angular relationship between said shaft and said plunger to thereby vary the fuel amounts delivered by said pump.

1l. The combination set forth in claim 12 wherein the angularly adjustable connection between said shaft and plunger comprises a sleeve supported in an axial bore in said shaft and having a slot extending parallel to the rotary axis thereof and a slot extending at an oblique angle to said axis, a stud fixed to said shaft and extending into said oblique slot, and 4a member rotatable with said plunger and having a portion extending into said parallel slot.

12. A fuel injection pump for a multi-cylinder internal combustion engine comprising a, cylinder having an inlet and by-pass passageway, a plurality of discharge passageways, a plunger working in said cylinder, means formed on said plunger for successively placing said discharge passageways in communication with the pressure space of said cylinder in intermittently successive positions of the rotary and reciprocating movement of said plunger, and means formed on said plunger for placing said pressure space in communication with said inlet and by-pass passageway during the suction and pressure strokes of said plunger, said plunger recipnocating and rotating means comprising a shaft adapted to be driven by or in unison with said engine, a cam operated by said shaft for reciprocating said plunger, and a connection between said shaft and plunger for rotating the latter, said connection comprising a sleeve supported by said drive shaft for rotary and axial sliding movement relative thereto, an axially slidable but non-rotatable connection between said sleeve and plunger, and a pin-and-helical slot connection between said shaft and sleeve.

13. The combination set forth in claim 12, wherein said sleeve is automatically shifted axially of said shaft by means responsive to the speed of rotation thereof to vary the angular relationship of said plunger and shaft.

14. The combination set forth in claim 12. wherein said sleeve is automatically shifted axially of said drive shaft by a governor comprising weights pivotally supported on said shaft and operable under the action of centrifugal force from the axis thereof to move said sleeve axially in one direction, a spring-pressed lever for yieldably resisting such movement of said sleeve, and means for varying the resistance offered by said spring-pressed lever to such movement of said sleeve.

15, 'I'he combination set forth in claim 12, wherein said sleeve is automatically shifted axially of said shaft by a governor comprising weights pivotally supported on said shaft and operable under centrifugal force from the axis thereof to move said sleeve axially in one direction, a lever mounted for swinging movement lengthwise of said sleeve with one end in position to be operated by such axial movement of said sleeve. an arm mounted for swinging movement lengthwise of said sleeve, a coil compression spring interposed between said arm and the other end of said lever for yieldably resisting movement thereof by said sleeve, a tension spring avranno associated with said arm and said compression spring for varying the resistance offered by said compression spring to movement of said lever by said sleeve.

16. The combination set forth in claim 12, wherein said sleeve is automatically shifted axially of said shaft by a governor comprising weights pivotally supported on said shaft and operable under centrifugal force from the axis thereof to move said sleeve axially in one direction, a lever mounted for swinging movement lengthwise of said sleeve with one end in position to be operated by such axial movement of said sleeve, an arm mounted for swinging movement lengthwise of said sleeve, a coil spring interposed between said arm and the other end of said lever for yieldably resisting movement thereof by said sleeve, a, tension spring having one end sustained by the free end of said arm. and means cooperating with the other end of said tension spring for varying the tension thereof and the angular relation thereof to the pivotal axis of said arm.

17. The combination set forth in claim 12. wherein said sleeve is automatically shifted axially of said shaft by a governor comprising weights pivotally supported on said shaft and operable under centrifugal force from the axis thereof to move said sleeve axially in one direction, a lever mounted for swinging movement lengthwise of said sleeve with one end in position to be operated by such `axial movement of said sleeve, an arm mounted for swinging movement lengthwise of said sleeve. an extensible link extending between said arm and the other end of said lever, a. coil compression spring mounted around said link for pressing the ends thereof against said arm and said other end of said lever, a tension spring having one end sustained by the free end of said arm, and a shaft disposed parallel to the pivotal axis' of said arm and connected to the other end of said tension spring for varying the tension thereof and the angularity thereof relative to said arm and said coil compression spring.

18. The combination set forth in claim 12, wherein said sleeve is automatically shifted axially of said shaft by a governor comprising a spider mounted on said shaft, a circumferentially yieldable driving connection between said shaft and spider, weights pivotally supported on said spider and operable under centrifugal force from the axis thereof to move said sleeve axially in one direction, a lever mounted for swinging movement lengthwise of said sleeve with one end in position to be operated by such axial movement of said sleeve, a fixed knife edge,an arm mounted on said knife edge for swinging movement lengthwise of said sleeve, an extensible link extending between said arm and the other end of said lever, a coil compression spring mounted around said link for pressing the ends thereof against said arm and said other end of said lever, a coil tension spring having one end sustained by the free end of said arm, and a manuaily operable shaft disposed parallel to said knife edge and connected to the other end of said tension spring for varying the tension thereof and the angularity thereof relative to said arm and said compression spring.

HERBERT C. EDWARDS.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 1,791,600 Onions Feb. 10, 1931 ,1,966,694 Vandet et al July 17, 1934 2,145,379 Vogelei et al J an. 31, 1939 2,372,559 Edwards Mar. 27, 1945 

